EP2414180A1

EP2414180A1 - Elastomeric joint

Info

Publication number: EP2414180A1
Application number: EP10720248A
Authority: EP
Inventors: Cengiz Erdogan; Richard Partyka
Original assignee: TRW Automotive GmbH
Current assignee: ZF Automotive Germany GmbH
Priority date: 2009-04-03
Filing date: 2010-03-30
Publication date: 2012-02-08
Anticipated expiration: 2030-03-30
Also published as: CN102448747A; KR20120005010A; US20120107038A1; DE102009016139A1; WO2010112006A1; EP2414180B1; US8770884B2; ES2525560T3; CN102448747B

Abstract

The invention relates to an elastomeric joint (10), having a housing (12) with a through opening (14) which extends axially along the longitudinal axis (16) of the elastomeric joint, a pivot (18) which extends through the through opening (14) of the housing (12), an elastomer body (20) which is fastened to the pivot (18) and is arranged radially between the pivot (18) and the housing (12), and with at least one supporting ring (22) which is fastened to the elastomer body (20) on one end side of the through opening (14), wherein a wire ring (32) locks the supporting ring (22) with respect to the housing (12), with the result that the pivot (18) is held in the housing (12) in an axially secured manner.

Description

elastomer joint

The invention relates to an elastomer joint, in particular for chassis parts of motor vehicles, according to the preamble of claim 1.

Elastomer joints are maintenance-free, insensitive to external environmental influences and are used especially in the automotive industry for precise axle guidance as well as for increasing ride comfort. In such elastomer joints, an elastic elastomer body is biased in the axial direction, resulting in an adjustable radial spring detection.

DE 37 15 360 C2 shows a generic elastomer joint in which a sleeve-shaped elastomer body is biased between two support rings. On the inner peripheral surface of a cylindrical housing material recesses are provided in a central zone, so that a space is created, in which the elastomeric body can escape. As a result, the bias of the elastomer body is reduced in this area, resulting in a progressive load with progressive load recognition. For axial securing of the elastomeric body within the housing, one of the two support rings is supported against an inner shoulder of the housing, wherein the other support ring is held by a snap ring inserted in the joint assembly.

The snap ring, which is used for example in the elastomer joint according to DE 37 15 360 C2, is also known as the so-called "Seeger ring". The Seeger ring is characterized by the fact that it is available as a standard part very reasonably priced on the market and allows easy disassembly of the elastomer joint. However, the Seeger ring is subject to the disadvantage that due to its rectangular cross-section under axial loads a tilting moment acting on him, resulting in a Ausknüpfen the Seeger ring from a groove formed in an inner peripheral surface of the housing, can lead. At least such a tilting moment leads to frequent axial displacements of the Seeger ring, whereby fatigue fractures may occur in the support ring which is in contact with the Seeger ring. Another disadvantage of the Seeger ring is that its circular coverage is only about 270 °, which can also result in the risk of Ausknüpfens.

Accordingly, the invention has the object to provide an elastomer joint with simple and robust locking means.

The object is achieved by an elastomer joint having the features of claim 1. Advantageous developments of the invention are defined in the dependent claims.

An elastomeric joint according to the invention is particularly suitable for use in vehicle parts of motor vehicles, and comprises a housing with a through opening extending axially along the longitudinal axis of the elastomeric joint. Further, the elastomeric joint includes a pivot extending through the through opening of the housing and an elastomeric body secured to the pivot and disposed radially between the pivot and the housing. A support ring is attached to an end face of the passage opening on the elastomeric body or on the pivot pin, wherein a locking element locks the support ring relative to the housing, so that the pivot pin is held axially secured in the housing. The locking element is formed from a wire ring.

The use of the wire ring in a function as a locking element, by means of which the support ring is locked relative to the housing, has the advantage that due to the suitable cross section of such a wire ring especially with an axial load of the pivot pin no tilting moments occur, resulting in a Ausknüpfen or Lead loose the wire ring. The wire ring can be made from a conventional spring steel be, which is advantageous in low manufacturing or procurement costs reflected.

In an advantageous embodiment of the invention, the wire ring may have a substantially circular cross-section. Semi-finished products with such a cross section are available in large quantities and correspondingly inexpensive. A circular cross-section prevents as above the emergence of a tilting moment and also ensures sufficient coverage with an adjacent wall of the housing. Alternatively, the wire ring may also have another suitable cross-section, in which case in any case no tilting moment is caused when the elastomer joint is loaded in the same way as in the case of the circular cross section. A polygonal or oval cross section is suitable for this purpose. A polygonal cross-section of the wire ring is preferably in the shape of a triangle, with a tip of this triangle directed towards the adjacent face of the through-hole and an orthogonal extending through this tip and referring to the apex-facing base of the triangle with the longitudinal axis of the elastomeric joint includes an angle of less than 90 °. The same applies mutatis mutandis for the oval cross-section, the longitudinal axis in the direction of the adjacent end face of the passage opening and with the longitudinal axis of the elastomeric joint forms an angle smaller than 90 °.

In an advantageous development of the invention, an inner peripheral surface of the housing may have a groove whose contour is adapted to the cross section of the wire ring. As a result, the wire ring in the mounted state fits harmoniously against the inner peripheral surface of the housing, without jamming or the like occurring. Such a groove can be inexpensively pretend in the inner peripheral surface of the housing, for example, by a machining process or directly in the prototyping of the housing, for example as a casting. In all of the above-mentioned possible cross-sectional shapes for the wire ring, there is the advantage that, in particular with axial load of the elastomer joint of the wire ring is pressed into the groove, without causing a tilting moment and / or an axial Moving the wire ring arise. Thus, an undesirable Ausknüpfen or even fatigue fractures can be effectively avoided on the support ring.

In an advantageous embodiment of the invention, the wire ring may have a circular coverage of at least 300 °, and in particular a circular coverage of at least 340 ° or even more. Such a circle coverage is in any case greater than that of a Seeger ring. This leads to the advantage that the displacements of the free ends of the wire ring at an axial load of the pivot pin are smaller, whereby the contact points of the support ring at the free ends of the wire ring are less stressed. As a result, thus fatigue fractures of the support ring can be avoided. Comparative tests have shown that at the same loads in the axial direction an elastomer joint with wire ring had no breakage on the support ring, whereas a comparable embodiment with Seeger ring showed fracture phenomena on the support ring.

In an advantageous development of the invention, the wire ring can be in contact with a contact surface of the support ring, wherein this contact surface encloses an angle of substantially 45 ° with the longitudinal axis of the elastomer joint. Such an angle of the contact surface of the support ring relative to the longitudinal axis of the elastomer joint has the advantage that at an axial load of the pivot pin or the elastomer joint has a force resulting suitably radially in the direction of formed within the inner peripheral surface of the housing groove. As a result, a Ausknüpfen the wire ring from the groove is effectively prevented, so that a secure positioning of the pivot pin is ensured within the housing in the axial direction.

In an advantageous embodiment of the invention, the support ring adjacent to the contact surface have a bulge, which has a vertex in the direction of the end face of the passage opening. A distance between this vertex and a point at which the groove merges into the inner peripheral surface of the housing is smaller than the diameter of the wire ring selected. This leads to the advantage that the wire ring is prevented with the elastomer joint mounted because of the too narrow passage between the vertex and the wall of the inner peripheral surface from emigrating towards the front side of the through hole. This additionally prevents unwanted untangling of the wire ring and thus increases the reliability.

In an advantageous embodiment of the invention, the support ring may be formed from a sheet metal stamping. This has an advantageous effect on the production costs. Such a stamped sheet metal part can be produced in one working step, including the above-mentioned angled abutment surfaces, without subsequently requiring reworking or the like.

The elastic elastomer body is always axially biased in the assembled state, resulting in a predetermined or desired spring rate of the elastomeric joint. This bias can be achieved in that the elastomeric body is clamped between the support rings. Here, the support rings may be attached directly to the pivot pin, wherein they comprise the elastomeric body on both sides at its axial end faces in the manner of a lid. In such an embodiment, a torsional movement of the elastomeric body is ensured with respect to the housing. Alternatively, the support rings may be attached directly to the elastomeric body, e.g. by vulcanization. Here, the support rings are radially fixed or vulcanized on an outer peripheral surface of the elastomer body. This allows both a torsional movement of the elastomer body relative to the housing and a gimbal tilting movement in a certain angular range relative to the longitudinal axis of the elastomer joint, for example in an angular range of 15 °.

In an advantageous embodiment of the invention, the housing may have an externally accessible bore, which opens adjacent to the wire ring. Through this hole, an auxiliary tool can be introduced, for. As, a mandrel or the like, the tip then comes into contact with at least one free end of the wire ring. By means of this auxiliary tool is a purposeful Unbolt the wire ring out of the groove to disassemble the elastomer joint if necessary.

In an advantageous embodiment of the invention, a support ring may be provided on both end sides of the passage opening, which is locked in each case by a locking element in the form of the wire ring relative to the housing. This leads to the advantage that an inner circumferential surface of the housing can be formed symmetrically, which leads to cost advantages. In other words, in such an embodiment, the pivot pin is fixed on both sides in the region of the respective end face of the passage opening by means of a wire ring on the housing. Thus, it is not necessary to provide within the housing a shoulder portion or the like, on which otherwise a support ring would abut for axial fixation.

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

The invention is illustrated schematically below with reference to an embodiment in the drawing and will be described in detail with reference to the drawing.

Show it:

1 shows an inventive elastomeric joint in a lateral

Cross-sectional view

FIG. 2 shows an enlarged view of the region I of FIG. 1,

FIG. 3 shows an enlarged view of the region I of FIG. 1, in a modified embodiment,

FIG. 4. a partial region of the elastomer joint according to FIG. 1, with respect to which an axial load case is shown,

FIG. 5 shows an enlargement of the area A of FIG. 4, Figure 6 is a plan view of a wire ring of the invention

Elastomer joint,

FIG. 7 is a side view of the wire ring of FIG. 6;

FIG. 8 shows a further embodiment of the invention

Elastomeric joint in a side cross-sectional view,

FIGS. 9a, 9b show side views of a part of the elastomer joint according to FIG. 1 and FIG. 8 respectively, wherein alternative cross-sectional shapes for a wire ring are shown,

Figure 10 shows an inventive elastomeric joint in a lateral

Cross-sectional view according to another embodiment,

Figure 11 is a conventional elastomeric joint in a lateral

Cross-sectional view

FIG. 12 shows a top view of a locking element in the form of a conventional Seeger ring,

FIG. 13 shows a side view of the Seeger ring according to FIG. 12,

FIG. 14 shows an enlarged view of the region II of FIG. 11 in an axial load case, and FIG

Figure 15 is an enlarged view of the area III of Figure 11 at

Action of an axial load.

FIG. 11 shows a conventional elastomer joint 1 in a lateral cross-sectional view. The elastomeric joint 1 has a housing 12 with a through-opening 14 which extends axially along a longitudinal axis 16 of the elastomeric joint 10. A pivot pin 18 extends through the passage opening 14 and is received in this. On an outer peripheral surface of the pivot pin 18, an elastomeric body 20 is fixed, which rests with its outer peripheral surface in the central region of the elastomeric joint 1 on an inner peripheral surface of the housing 12. The elastomeric body 20 may be fixed to the hinge pin 18 or to the inner peripheral surface of the housing 12 by scorching, gluing or the like. By means of the elastomer body 20 is a movement of the pivot pin 18 relative to the housing 12 rotato- rally about the longitudinal axis 16 and / or gimbal, ie by means of a tilting movement about the longitudinal axis 16, possible.

On the elastomeric body 20, an upper support ring 22 and a lower support ring 24 are fixed in the region of the two end faces of the through opening 14, for example by scorching, gluing or the like. By means of the support rings 22, 24, the elastomeric body 20 is axially, i. in the direction of the longitudinal axis 16, biased. The lower support ring 24 is seated on a shoulder portion 26 on the inner peripheral surface of the housing 12 so as to be axially positioned. The upper support ring 22 is secured by a locking element 28 in the form of a snap ring (also known as a "Seeger ring"), which is shown in Figure 12 in a plan view and in Figure 13 in a side view individually. The Seeger ring 28 engages in the mounted state in a groove 30 which is formed in the inner peripheral surface of the housing 12. When Seeger ring 28 is mounted thus also the upper support ring 22 is positioned axially within the housing 12. In the assembled state according to the illustration of FIG. 11, the pivot pin 18 is thus secured against falling out of the housing 12.

The axial fixation of the upper support ring 22 within the housing 12 by means of the Seeger ring 28 is disadvantageous in that the Seeger ring 28 can untangle from a certain load height of the elastomeric joint 1 from the groove 30. FIG. 15 shows the region III of FIG. 11 when an axial load acts on the pivot pin 18 and thus also on the Seeger ring 28. In FIG. 15, arrows represent the force direction or the resulting forces acting on the Seeger ring 28 under axial load. FIG. 14 shows the region II of FIG. 11, and corresponds in mirror image to the representation of FIG. 15. FIG. 14 shows the process of detaching the Seeger ring 28 from the groove 30 as a result of an axially acting force F _3x . Because of the rectangular cross section of the Seeger ring 28, the axial force F _ax causes a tilting moment acting on the Seeger ring 28, which ultimately has the uncoiling of the Seeger ring 28 result. Damage to the elastomeric joint 1 may occur, on the one hand, in that the Seeger ring 28, as shown in FIG. 14, uncouples from the groove 30, so that the upper support ring 22 is no longer secured inside the housing 12. A further possibility of damage in the elastomeric joint 10 according to FIG. 11 is that fatigue fractures occur in the upper support ring 22 in the regions which are in contact with the two free ends of the Seeger ring 28. Such fatigue fractures result from an axial loading of the pivot pin 18 leading to small axial displacements of the Seeger ring 28, especially in the region of its two free ends. Such displacements are assisted in that the Seeger ring 28, as shown in Figure 12, has a circular coverage of approximately 270 ° so that the free ends are relatively widely spaced. This distance is indicated in FIG. 13 by the distance L2. Overall, thus subject to the axial securing of the upper support ring 22 by means of the Seeger ring 28 because of the aforementioned damage opportunities low reliability.

FIG. 1 shows an elastomer joint 10 according to the invention in a lateral cross-sectional view. This joint corresponds in its essential structure to the joint of Figure 8 - essential components are provided with the same reference numerals and not explained again to avoid repetition.

An essential difference of the elastomeric joint 10 according to FIG. 1 compared with the conventional elastomeric joint 1 according to FIG. 11 is the securing of at least one of the two support rings. Instead of a Seeger ring 28, the upper support ring 22 is axially secured in the housing 12 by means of a wire ring 32 in the elastomer joint of Figure 1. The wire ring 32 may be made of a conventional spring steel or the like. Accordingly, the production of this wire ring or its procurement is very inexpensive. FIG. 2 shows the region I of FIG. 1 in an enlarged view. The upper support ring 22 has adjacent to its outer peripheral surface a contact surface 34 which is in contact with the wire ring 32. On a Innenumfangsflä- surface 36 of the housing 12, a groove 38 is formed, whose contour is adapted to the substantially circular cross-section of the wire ring. Thus, in the assembled state, the wire ring 32 nestles harmoniously in the groove 38, without jamming or the like occurring.

In FIGS. 3 and 4, the region I of FIG. 1 is shown in an enlarged view. FIG. 3 illustrates that the contact surface 34 encloses an angle of 45 ° with the longitudinal axis 16 (or with a parallel to the longitudinal axis 16). In other words, a surface of the abutment surface 34 is inclined relative to the longitudinal axis 16 by an angle of 45 °. Figure 4 illustrates the advantageous effect of this angular relationship. Upon the occurrence of an axial force F _ax , which acts on the pivot pin 18 and thus also on the upper support ring 22, the wire ring 32 experiences a resultant force F _re s, which is directed in the direction of the groove 38. Accordingly, the wire ring 32 is pressed by the force Fr _es in the groove 38, so that an automatic untangling of the wire ring 32 from the groove 38 at an axial load of the elastomeric joint 10 is not possible. As a result, the reliability of the elastomer joint 10 is substantially improved.

It is understood that the above-mentioned angle of 45 ° between the abutment surface 34 and the longitudinal axis 16 can also assume other values, for example greater or less than 45 °. For this angle is only important that it is suitably chosen so that at a force acting on the wire ring 32 load (in the radial and / or axial direction) the force resulting Fre _s is facing in the direction of the groove 38 so that a Ausknüpfen of the wire ring 32 is prevented.

FIG. 5 shows the region A of FIG. 4 in an enlarged view. For simplicity, the wire ring 32 is not shown here. The upper support ring 22 has adjacent to the contact surface 34 has a bulge 44 which in the direction the adjacent end face of the through hole 14 has a vertex 46. The distance between this vertex 46 and a point 48 at which the groove 38 merges into the inner peripheral surface 36 of the housing 12, determined as a distance s. It is important that the distance s is chosen smaller than the diameter of the wire ring 32. In the assembled state, this is also shown in the illustrations of Figure 2 and Figure 4. By the distance s is chosen smaller than the diameter of the wire ring 32, the wire ring can not untie from the groove 38 for geometric constraints.

The wire ring 32 is shown in Figure 6 in a plan view. FIG. 7 shows this wire ring 32 in a side view. The wire ring 32 has a circle coverage of about 340 °, and accordingly, the distance between the two free ends of the wire ring 32 (shown in Figure 6 by the distance L1) is smaller than the distance between the two free ends of the Seeger ring 28 (according the distance L2 of FIG. 10). The smaller distance between the two free ends of the wire ring 32 to each other or its larger circular coverage as compared to the Seeger ring also leads to greater reliability, since the two free ends of the wire ring 32 are subject to lower axial displacements in the presence of axial loads. Furthermore, because of the round cross-section of the wire ring 32, no starting or tilting moments in the region of the groove 38 occur, as a result of which the axial securing of the upper support ring 22 within the housing 12 is further improved.

Similar to the embodiment of FIG. 11, in the embodiment of FIG. 1, the lower support ring 24 rests on a shoulder portion 26 formed on an inner circumferential surface of the housing 12. As a result, the lower support ring 24 is fixed axially with respect to the housing 12. In deviation from the embodiment shown in Figure 1, however, a lower support ring can be used, which is identical to the upper support ring 22. In correspondence with the abutment surface 34 of such a support ring, a suitable chamfer or the like would then be provided in the lower region of the housing 12 instead of the shoulder portion 26, against which this abutment surface 34 abuts. The use of structurally identical support rings brings along savings the significant advantage that thereby simplifies assembly of the elastomeric joint 10, because a confusion of different support rings is excluded.

FIG. 8 shows another embodiment of the elastomeric joint 10. In contrast to the embodiment of FIG. 1, in the embodiment of FIG. 8 both the upper support ring 22 and the lower support ring 24 are both axially secured by a wire ring 32. The embodiment of the support rings and the complementary grooves in the embodiment of Figure 8 corresponds to the illustration of Figure 2, so that reference is made to avoid repetition. The embodiment of Figure 8 has the advantage that an inner circumferential surface of the housing 12 is formed completely symmetrical to the transverse axis 40 of the elastomeric joint 10, since the shoulder portion 26 (see Figure 1) is omitted. In the embodiment of Figure 8, the upper and lower support ring 22, 24 may consist of equal parts, which has a favorable effect on the manufacturing cost.

FIGS. 9a and 9b show enlarged partial regions of the elastomeric joint 10 relative to the region I of FIG. 1, wherein the wire ring 32 here has an alternative cross section, namely in the form of a triangle (FIG. 9a) or in the form of an oval (FIG. 9b). , In the triangular cross-sectional shape, the apex of the triangle points toward the adjacent end face of the through-hole 14, with an orthogonal 52 passing through the apex of the triangle and referring to a tip-facing base side with the longitudinal axis 16 (or a parallel 16) 'to) an angle α includes. The same applies to the wire ring 32 with oval cross-section (Figure 9b), wherein a longitudinal axis 54 of this oval with the longitudinal axis 16 of the elastomeric joint 10 (or a parallel 16 'to) includes an angle ß. The angles α and β are each smaller than 90 °.

It is understood that in the embodiments of the wire ring 32 according to the figures 9a and 9b, the groove 38 which is formed on the inner peripheral surface 36 of the housing 12, complementary to the cross section of the wire ring 32nd is trained. Accordingly, this results in the same advantages as in the circular cross-sectional shape of the wire ring according to Figure 4, after which a force results in stresses of the wire ring 32 always in the direction of the groove 38 and therefore a Ausknüpfen the wire ring 32 is effectively prevented.

FIG. 10 shows a further modification of the elastomer joint 10. The only difference compared to the embodiment according to FIG. 1 is that a lateral bore 50 is provided in the housing 12 and is accessible on the outside. The bore 50 leads radially inwardly and opens adjacent to the wire ring 32. By means of the bore 50, a disassembly of the elastomeric joint 10 can be made if necessary. This is done by first urging the upper support ring 22 forcibly axially inwardly, i. is displaced in the direction of the lower support ring 24, against the bias of the elastomer body 20. As a result, the wire ring 32 is released in the region of the passage opening 14 of the upper support ring 22. Subsequently, an auxiliary tool, for example in the form of a dome, be introduced through the bore 50 from the outside, in which case the wire ring 32 with the tip of this mandrel can be levered out of the groove 38. Preferably, the tip of the mandrel comes into contact with the wire ring 32 in the region of one of its free ends.

The elastomeric joint 10 according to the invention has an improved performance compared to a conventional elastomer joint in that even with larger axial or radial loads no damage to the joint (for example in the form of a disengagement of the wire ring or breakage on the support ring) occur. In addition, the provision of the wire ring 32 is possible with extremely inexpensive means, wherein the known per se structure of an eggastomer joint for use of such a wire ring requires only minor modifications.

Claims

An elastomeric joint (10), in particular for chassis parts of motor vehicles, comprising a housing (12) having a through opening (14) extending axially along the longitudinal axis (16) of the elastomeric joint (10), a pivot pin (18) extending through the through-opening (14) of the housing (12) extends, an elastomeric body (20) attached to the pivot pin (18) and disposed radially between the pivot pin (18) and the housing (12) and at least one support ring (22). mounted on an end face of the through hole (14) on the elastomeric body (20) or on the pivot pin (18), wherein a locking element locks the support ring relative to the housing (12) so that the pivot pin (18) in the housing (12) 12) is held axially secured, characterized in that the locking element is formed of a wire ring (32).

The elastomeric hinge (10) of claim 1, wherein the wire ring (32) has a substantially circular cross-section.

3. elastomeric joint (10) according to claim 1, wherein the wire ring (32) has a substantially oval cross-section, wherein the longitudinal axis (54) of the oval in the direction of the adjacent end side of the through hole facing and with the longitudinal axis (16, 16 '). of the elastomeric joint (10) encloses an angle (β) smaller than 90 °.

The elastomeric hinge (10) of claim 1, wherein the wire ring (32) has a polygonal cross-section.

5. An elastomeric joint (10) according to claim 4, wherein the wire ring (32) has a triangular cross section, wherein a tip of the triangular cross section is directed towards the adjacent end face of the through hole and an orthogonal (52) passing through this tip and refers to the opposite side of the base of the triangular cross-section, with the longitudinal axis of the elastomeric joint (10) forms an angle (α) smaller than 90 °.

The elastomeric hinge (10) of any one of claims 1 to 5, wherein the wire ring (32) is in contact with an abutment surface (34) of the support ring (32), said abutment surface (34) being integral with the longitudinal axis (16) of the elastomeric joint (10) includes an angle of substantially 45 °.

7. elastomeric joint (10) according to one of claims 1 to 6, wherein an inner peripheral surface (36) of the housing (12) has a groove (38) whose contour is adapted to the cross section of the wire ring (32).

The elastomeric hinge (10) of claim 7, wherein the upper support ring (22) adjacent the abutment surface (34) has a convexity (44) with a vertex (46), wherein a distance (s) between the apex (46) and a position (48) at which the groove (38) merges into the inner peripheral surface (36) of the housing (12) is smaller than the diameter of the wire ring (32).

9. elastomeric joint (10) according to any one of claims 1 to 8, wherein the wire ring (32) has a circular coverage of at least 300 °.

10. elastomeric joint (10) according to claim 9, wherein the wire ring (32) has a circular coverage of at least 340 °.

11. elastomeric joint (10) according to one of claims 1 to 10, wherein the support ring (22, 24) is formed from a sheet metal stamping.

The elastomeric hinge (10) of any one of claims 1 to 11, wherein the support ring (22, 24) is secured to the elastomeric body (20).

13. elastomeric joint (10) according to claim 12, wherein the support ring (22, 24) on the elastomeric body (20) is vulcanized.

14. An elastomeric joint (10) according to any one of claims 1 to 13, wherein the housing (12) has an externally accessible bore (50) which opens adjacent to the wire ring (32).

15. elastomeric joint (10) according to one of claims 1 to 14, wherein at both end sides of the passage opening, a support ring (22, 24) is provided, each locked by a locking element in the form of the wire ring (32) relative to the housing (12) is.